Fluid applying mechanism



April 28, 1970 R. KQNORTON FLUID APPLYING MECHANISM 3 Sheets-Sheet 1 Original Filed Oct. 19. 1965 FIG.2

IN VEN TOR.

K. NORTON ROBERT ATTORNEYS vApril 28, "1970 h R. K. NORTQN 3,508,489

FLUID APPLYING MECHANISM Original Filed Oct. 19, 1965 5 Sheets-Sheet 2 INVENTOR.

ROBERT K. NORTON BY ATTORNEYS April 28, 1970 R. K. NORTON 3,503,489

7 FLUID APPLYING MECHANISM Original Filed Oct. 19. 1965 3 Sheets-Sheet 5 IN VENT OR.

ROBE RT K. NORTON @WMW ATTORNEYS United States Patent FLUllD APPLYING MECHANISM Robert K. Norton, Twinsburg, Ohio, assignor to Harris- Intertype Corporation, Cleveland, Ohio, a corporation of Delaware Continuation of application Ser. No. 497,824, Oct. 19,

1965. This application May 15, 1969, Ser. No. 840,082 Int. 'Cl. B411 25/02 US. Cl. 101148 7 Claims ABSTRACT OF THE DISCLOSURE A lithographic printing press in which an ink coated first roll, e.g., a resilient form roll running in engagement with the printing plate mounted on a plate cylinder, has dampening fluid supplied thereto from a second roll which runs in engagement with the first roll with the first and second rolls being resilient surface rolls. The rolls are ink receptive and the second roll is driven at a speed different from the first roll to control the amount of dampening fluid transferred to the first roll, the first roll being driven at the surface speed of the plate. The second roll is driven by drive means which includes an overrunning device so that the first roll can drive the second roll at a speed faster than the drive to the second roll but if this occurs, a brake mechanism responsive to the overdriving effects a braking of the second roll to the speed of the drive means. If the overdrive is suflicient, a switch is tripped to perform a control function in addition to the braking. A hydrophylic surface roll runs in engagement with the second roll and operates at the same surface speed of the second roll and dips into a reservoir of dampening fluid contained in a pan to supply dampening fluid to the second roll. The first roll has a nonoperative position away from the plate and the second roll can be moved to and from the engagement with the first roll when the latter is in its non-operative position and is moved to engagement with the first roll to move the latter to an operating position against the plate. The third roll can be moved to and from engagement with the second roll regardless of the position of the latter.

This application is a continuation of application Ser. No. 497,824, filed Oct. 19, 1965.

The present invention relates to a lithographic printing press and more particularly to a dampening system for applying dampening fluid to the surface of a printing plate in such a press.

One commercial method of dampening a lithographic printing plate utilizes a variable speed dampening roll which runs in engagement with a form roll to apply dampening fluid to the printing plate, the speed of the dampening roll being varied to control the amount of dampening fluid applied.

An important object of the present invention is to provide a new and improved method and apparatus for applying dampening fluid to the surface of a lithographic printing plate which provides better control of the dampening fluid than those systems presently available.

Another object of the present invention is to provide a dampener using a variable speed roll in which the differential speed between the roll and a cooperating roll is not as critical as in existing arrangements.

A further object of the present invention is to provide a new and improved method and apparatus for applying dampening fluid to a lithographic printing plate in which dampening fluid is applied to an ink covered roll, the surface speed of which is different from, and preferably adjustable relative to, the surface speed of a cooperating ink covered roll to control the amount of dampening fluid applied to the press.

A further object of the present invention is to provide a method and apparatus for applying dampening fluid to a lithographic printing plate in which a transfer roll runs at a diflerent speed from the roll receiving the dampening fluid therefrom and in which the surface speed of the transfer roll for a given speed of the receiving roll may be adjusted over a substantial range without losing control.

A still further object of the present invention is to provide a new and improved dampening mechanism or other coating mechanism in which a transfer roll is driven at a different speed preferably less than a cooperating roll which receives material from the transfer roll with the drive to the transfer roll being so constructed and arranged that if the cooperating roll tends to overdrive the drive to the transfer roll, a control operation will be performed to maintain speed of the transfer roll and preferably protect the rolls if the overdrive exceeds a predetermined torque.

Yet another object of the present invention is to provide a new and improved printing press having a dampening system in which the surface of a roll having an elastomeric peripheral portion tends to be driven at one speed by a cooperating member running in engagement with the surface of a cooperating rotating member and wherein a drive to the roll effects rotation of the roll at a different and slower speed than the surface speed of the cooperating member with the drive being so constructed and arranged that it will be overrun when the roll rotates at a speed higher than the drive speed and so that the roll will be braked to slow the roll to the drive speed with a trip 01f function preferably being performed if the overdrive exceeds a predetermined torque.

It is also an object of the present invention to provide a coating mechanism in which cooperating elastomeric rolls running in engagement with each other are operated at different surface speeds to control the application of a non-lubricating type coating fluid and a lubricating fluid is supplied to the rolls to provide a lubrication of the slippage between the rolls.

A further object of the present invention is to provide a new and improved method and apparatus in which a transfer roll which transfers dampening fluid to a form roll is driven by a drive separate from the drive for the form roll and in which the transfer roll is braked if the form roll overruns the drive for the transfer roll, the mechanism preferably operating to perform a control function if the overdrive exceeds a predetermined torque.

Further objects and advantages of the present invention will be apparent to those skilled in the art to which it relates from the following detailed description of the preferred embodiment thereof made with reference to the accompanying drawings forming a part of this specification and in which:

FIG. 1 is a diagram-matical view of a portion of a lithographic printing press embodying the present invention;

FIG. 2 is a modification of the present invention;

FIG. 3 is an elevational view of the dampening mechanism of FIG. 1 having portions schematically illustrated portions in section and portions removed;

FIG. 4 is a sectional View of the dampening mechanism taken approximately at line 44 of FIG. 3 and having portions removed;

FIG. 5 is a fragmentary sectional view of a portion of a driving mechanism for the dampener of FIG. 4;

FIG. 6 is a fragmentary sectional view of a portion of the driving mechanism taken approximately at line 6-6 of FIG. 5; and

FIG. 7 is an elevational view of a portion of the dampening mechanism of FIG. 3.

While the present invention is susceptible of use in various coating machines, it is particularly designed for use in a printing press. Referring to the drawings, the present invention is illustrated in a lithographic printing press which is partially shown in FIG. 1 of the drawings.

As shown in FIG. 1, the printing press includes a plate cylinder 10 which is inked by a conventional inking mechanism 13, including form rolls 11. Dampening fluid is applied to the printing plate in advance of the ink by a dampening mechanism, designated generally by the reference numeral 14. The dampening mechanism 14 includes a form roll 16 adapted to rotate about its axis in rolling contact with the plate on the plate cylinder 10 and a transfer roll 17 which runs in engagement with the form roll 16 and rotates about its axis in a directionopposite to the direction of rotation of the form roll 16 so that the portions of the rolls which engage each other are moving in the same direction.

A metering roll 18 runs in engagement with the transfer roll 17 and rotates in a direction about its axis opposite to the direction of rotation of the transfer roll 17 so that the parts of the rolls which engage to form the nip between the rolls are moving in the same direction. The metering roll 18 is a roll having a hydrophylic, smoothly finished, hard unyielding surface, preferably chrome, which, in the illustrated embodiment, rotates through dampning fluid in a pan 20. The rotation of the hydrophilic roll 18 through the fluid in the pan 20 causes the surface of the roll 18 to pick up a film or coating of dampening fluid which is metered and transferred to the transfer roll 17 at the nip between the transfer roll and the metering roll 18.

The form roll and the transfer roll 17 have resilient surfaces which may be provided by a conventional elastomeric material, such as neoprene, conventionally used in inkers and dampening mechanisms to provide resilient surfaces. The rolls 16, 17 are oleophilic, that is, ink receptive, and during operation, both the form roll 16 and the transfer roll 17 will have an ink coating built up thereon as a result of running against the plate on the plate cylinder 10 which has been inked by the inking mechanism 13. The hydrophylic surface of the roll 18, however, is an ink rejecting surface and the roll 18 will operate as a clean roll. Consequently, during operation, the rotation of the metering roll 18 in the pan 20 causes the surface of the roll to pick up a coating of dampening fluid to be applied to the ink coated transfer roll 17 with the dampening fluid being metered and smoothed when it is applied to the transfer roll 17 by the pressure relationship between the rolls 17 and 18.

The form roll 16 is frictionally driven by the plate on the plate cylinder 10 so that the surface speed of form roll 16 is the same as the surface speed of the plate. The form roll 16 may also be positively driven from the press drive. The transfer roll 17, however, is driven at a surface speed different from the surface speed of the form roll 16, preferably at a slower speed, to control the amount of dampening fluid applied. It is preferable that the transfer roll 17 be driven at a speed which may be adjusted to enable the amount of dampening fluid applied to the plate to be adjusted by changing the surface speed of the roll 17 relative to the surface speed of the roll 16. The coating of ink on the rolls provides a lubrication for the slipping between the elastomeric rolls.

In the preferred and illustrated embodiment, the transfer roll 17 is driven from the metering roll 18 by gars 24a and 24b which are mounted on the shafts of the rolls 17 and 18 and the roll 18 is driven by a variable speed motor 25 positioned at the gear side of the press.

The roll 18 is driven by the motor 25 through a unidirectional clutch 30. The clutch has an input element 31 keyed to the shaft 29 of motor 25, and an output element 32 slidably keyed to a drive shaft 28 which carries a gear 26 in meshing engagement with a gear 27 on the shaft of roll 18. The output element 32 has limited slidability on the shaft 28 to allow the output element 32 to shift inwardly from its normal position on shaft 28 against the bias of a spring 34. The output clutch element 32 will shift inwardly if it is driven so as to overrun the drive from the input element 31. As will be explained hereinafter, the shifting of the output element 32 causes a braking of the overdrive to again re-establish a driving relationship between the clutch elements.

The clutch elements 31, 32 are shown in the form of a jaw clutch. The elements are generally circular in cross section and their adjacent ends are each formed to provide at least one driving tooth and preferably are formed to provide diametrically opposed driving teeth. As illustrated in FIG. 5, the clutch elements 31 and 3.2 each include four driving teeth. These driving teeth are identical in construction and therefore only one will be described in its relation with its clutch element and a tooth on the other of the clutch elements. The clutch element 31 has a driving tooth 35 with a circumferentially facing driving surface 35a which is formed between the ends of offset helical surfaces 37 formed on the input clutch element 31. The tooth surface 35a extends axially to join the helical surfaces 37, 38 and forms the driving surface of the tooth. The clutch element 32 has a tooth 36 with a driving surface 36a which is formed by similar offset helical surfaces 39, so that if the direction of relative rotation between the input and output clutch elements are such to move the driving surfaces 35a, 36a together, a driving relationship is established while if the direction of relative rotation is such as to move the surfaces 35a, 36a apart, no drive is established and the helical surfaces 37, 39 and the helical surfaces 38, 40 will cooperate to produce an axial movement of the clutch member 32 away from the clutch member 31. The illustrated clutch is basically the same as certain conventional overrunning clutches.

The overrunning feature of the output clutch element 32 is utilized to prevent the form roll 16 from driving the transfer roll 17 so as to overrun the drive from the variable speed motor 25. If the form roll 16 starts to overdrive the transfer roll 17 and the metering roll 18, the clutch 30 will overrun to cause the output element 32 to shift to the left, as viewed in FIG. 5, against the bias of spring 34, as described above, and when this occurs, a brake shoe mounted on the output element 32 of the clutch 30 Will engage a brake element 46 to brake the rotation of the transfer roll 17. When the speed of the transfer roll is braked, it will be slowed to where the variable speed motor will again effect the drive. In this manner, the speed of the transfer roll 17 is maintained substantially constant even though the form roll 16 tends to overdrive the motor 25. The extent of the axial movement of the clutch member 32 is preferably limited so that the teeth 35, 36 are always in axially overlapping relationship.

In the illustrated embodiment, the brake element 46 is supported about the drive shaft for limited rotation and is spring-urged by a spring 48 to a predetermined position against an adjustable stop 49. In the event that the torque of the overdrive is suflicient to overcome the spring 48, the spring will yield and the brake element 49 will rotate away from the stop and operate a switch 52 to trip the dampening mechanism, or the press, or to perform another control function. The switch 52 is preferably mounted for adjusting movement toward and away from the stop 49.

The performance of a trip function in the event that the overdrive exceeds a predetermined torque is particularly advantageous during the clean-up operation of the press. During the clean-up operation, the metering roll is normally dropped away from the transfer roll and a cleaning fluid is supplied to the inking mechanism. This fluid will distribute itself through the ink rolls and the ink coated rolls of the dampening mechanism to clean up the ink. Normally the ink provides a lubricating effect between the form roll and the transfer roll, but as the ink cleans up, the lubrication between the transfer roll and the form roll is reduced and damage to the elastomeric roll surfaces which slip relative to each other might result unless a trip off function is performed as the lubrication is reduced.

The overdrive torque can also be limited, if desired, by providing a friction drive adapted to slip on overload between the brake element 45 and the output clutch element 32. This can be in the nature of any type of conventional overload friction clutch.

In the illustrated and described embodiment, the form roll 16 is supported by a support member 57 which is pivoted at its lower end to a dampener frame member by a pivot pin 58. The transfer roll 17 is supported by a support member 60 pivotally supported on the frame member by a pivot pin 61. The metering roll 18 is supported by a pivoted member 62 which is pivoted coaxially with the pivoted member 60 about the pivot 61.

The form roll 16 is moved into and out of engagement with the plate cylinder by the operation of a cylinder 64 which is preferably pneumatically operated and which is connected between the dampener side frame and the upper end of the support member 57 as the latter is viewed in FIG. 3. Operation of cylinder '64 moves support member 57 about the axis of the pivot pin 58 at the lower end of the support member 57 by a connection 65 which includes a tie rod 66. The tie rod 66 is pivoted to the support member 60 and is received in and extends through a block 67 pivotally supported on the upper end of the support member 60. The end of the tie rod projecting outwardly from the block 67 and designated by the reference numeral 68 is threaded and has a stop member 69 threaded thereon for engaging the pivoted bloc-k 67, the stop member being backed up by a lock nut 70. The portion of tie rod 66 between the upper end of the support members 57, 60 has a coil spring 71 which surrounds the tie rod and which has ends abutting the pivot block 67 on the support member 60 and an adjustable nut 72 threaded onto the tie rod respectively.

When the cylinder 64 is operated to move the form roll 16 out of engagement with the plate, the support member 57 for the form roll will move about its pivot 58 and the tie rod connection will cause the transfer roll support member 60 to move about its pivot 61 which is offset to one side of and below the pivot 58. As the form roll and the transfer roll swing about their pivots, a clearance will be provided between the rolls because of the offset pivots. The 0 position of the rolls may be determined by an adjustable stop 73 which is engaged by a part of the support member 57. Similarly, when the cylinder 64 is operated to move the transfer roll 17 with the form roll 16 to an on position, the different pivot axes will cause the rolls to move into engagement with each other. When on the rolls will have a pressure engagement with each other controlled by the position of the threaded stop member 69 which determines the relative positions of the support members 57, 60. The on" position of the form roll 16 and its pressure relationship with the plate cylinder may be determined by an adjustable stop 74 which engages a part 75 on the member 57 to limit its movement toward the plate cylinder.

When the form roll 16 is in its off position, the transfer roll 17 may be brought into contact with the form roll by actuating a lever 83 without moving the form roll to its on position. The lever 83 is connected to an actuating block 82 which is pivoted for movement between an o position and a second position to cause a pin 84 on the block to engage the underside of a laterally projecting portion 80 on the support member 60 and move the support member 60 about the pivot pin 61. The spring 72 yields as the support member 60 moves 6 about its pivot and the transfer roll 17 moves into engagement with the form roll 16. The form roll 16 is held against movement by the spring 72 and by the cylinder 64.

The support member 62 for the metering roll 18 is connected to the support member 60 for the transfer roll 17 to cause the metering roll to move with the support member 60 and the transfer roll as they are moved about the pivot while maintaining that pressure relationship, but the connection therebetween is extensible to allow the metering roll to be dropped away from the transfer roll 17. Referring to FIG. 3, the metering roll support member 62 is connected to the adjacent member 60 by a generally vertical tie rod pivoted to a laterally projecting portion 88 on the member 62 below the projection of the support member 60 and extending between portion 88 and a block 90 pivoted at 91 to the support member 60 above the lateral projection 80 of the support member 60. The tie rod 86 has a pivot pin portion 92 extending laterally therefrom which is pivotally received in the block 90 so that the time rod will pivot about an axis parallel to but offset from the pivot axis 91 of the block 90. The block 90 is movable about its pivot 91 between two positions relative to the suport member 60 to raise and lower the tie rod 86 to move the metering roll between a position where the metering roll engages the transfer roll and a second position where it is out of engagement with the transfer roll. The guide block 90 is held in the selected one of its two positions relative to the support member 60 by a positioning member 95 which is pivoted to the guide block 90 for pivotal movement about an axis parallel to the pivot axis 91 and is disposed on the side of the tie rod connection 89 which is remote from the axis 91. The positioning member 95 engages the upper side of the laterally projecting portion 80 of the member 60 and can be rotated between two positions by means of a handle 97 to cause either a generally planar surface 98 or a generally planar surface 99 on the member 95 to engage the upper side of the portion 80. The surface 99 is angularly related to the surface 98 so that when member 95 is rotated such that surface 99 engages the projecting portion 80, the tie rod 86 is lowered relative to the laterally extending portion 80. This in turn lowers the support member 62 relative to the support member 60 by allowing the member 62 to move about the pivot 61 to drop the metering roll out of engagement with the transfer roll. When the handle 97 is operated to return the surface 98 into engagement with the upper side of the laterally projecting portion 80, the tie rod 86 is raised to move the metering roll into engagement with the transfer roll. The relationship of the metering roll and the transfer roll for the various positions of the lever 97 may be changed by adusting a threaded stop member 100 on the upper end of the tire rod 86 to increase or decrease the length of the tie rod between support member 62 and the tie block 97. This will also adjust the pressure relationship between the metering roll and the transfer roll. In the illustrated mechanism the tie rod 86 extends through a pivot block which is pivoted to the member 90 and is slidable therein. It will be appreciated by those skilled in the art that the weight of the metering roll and support member 62 will maintain the positioning member 95 in engagement with the laterally projecting portion 80.

Thus far the description has referred to the vertically extending support members 57, 60, 62 which are on the feed side of the press which is the remote side shown in FIG. 3. It will be understood that these members are duplicated at the other side of the dampener shown in FIG. 3 and are constructed and arranged in the same manner to support the ends of rolls at that side of the dampening mechanism. Similarly, the cylinder 64, the tie rods 66, 86, the block 82, and the positioning member 95 are also duplicated at the gear side of the dampening mechanism. Certain of these parts are shown in FIG. 4 and have been given the same reference numerals as the corresponding parts. The blocks 80 and the positioning members are, however, operated by handles which are manually disposed only on the feed side of the press and are not duplicated in the opposite or gear side of the press.

The end of the metering roll 18 on the feed side of the press may be shifted horizontally to skew the axis of the metering roll with respect to the axis of the transfer roll. As shown in FIG. 7, support member 62 mounts a bearing block 102 having a bearing therein which the adjacent end of the metering roll shaft is rotatably supported. Bearing block 102 includes pin members 103 connected thereto and which extend into elongated slots 104 formed in the member 62. This pin and slot arrangement limits movement of the end of the metering roll in a vertical direction but permits horizontal movement as the bearing block slides on a supporting surface 105 formed on the member 62. When the metering roll has been moved to provide the desired angularity with respect to the transfer roll, the bearing block 102 may be fixed against movement on the member 62 by a conventional locking mechanism which has not been shown in the drawings.

Skewing the metering roll with respect to the transfer roll, as described above, changes the angularity betweer the metering roll axis and the bearing blocks. To accommodate this angularity, the bearings in the bearing blocks are conventional self-aligning bearings which are constructed to swivel in the bearing blocks so as to accommodate the skewing of the roll shaft. It should be apparent that skewing of the metering roll, as described, will cause the gears 24a and 27 on the metering roll shaft to move slightly relative to the driving gear 26 and gear 24b on the transfer roll shaft. To prevent damage to the meshing gears as a result of misalignment due to skewing the metering roll, gears 24a and 27 on the metering roll are made of a stiflly resilient plastic such as nylon.

From the foregoing description, it can be seen that the transfer roll 17 can be brought into engagement with the form roll 16 while the latter is in. its off position and while in contact with the metering roll 18 so that the dampening fluid may be applied to the form roll and films formed on the surfaces of the metering roll, the transfer roll and the form roll before the form roll is moved into engagement with the plate. Similarly, the metering roll may be moved into or out of engagement with the transfer roll by operating the lever 97 when the transfer roll is in or out of engagement with the form roll.

While the form roll 16 has been described as a form roll of the dampening mechanism, it will be understood by those skilled in the art that the form roll might also be a form roll of the inker, and that when the form roll is moved into position with the plate cylinder it may also engage a vibrating roll 19 or other roll of an inker 13a as illustrated in FIG. 2 to function as the first form roll of the inker as well as the form roll of the dampening mechanism. In such an arrangement, as in the first described arrangement, both the form roll 16 and the transfer roll 17 will have an ink coating thereon. The vibrating rolls of the inker are conventionally driven from the press drive and the vibrating roll will also drive the form roll 16 at the surface speed of the plate through the en gaged peripheral surfaces of the rolls.

It has been found that a dampening mechanism embodying the present invention is not speed sensitive and only a small quantity of alcohol or the like need be used to obtain correct operation of an application of dampening fluid. Alcohol is commonly used in the dampening fluids applied by a dampening mechanism of a lithographic printing press to facilitate the obtaining of an even application of a thin film to the plate.

Having described the invention, the following is claimed.

1. In a lithographic printing press having a printing plate mounted on a rotatable plate cylinder, inking mechanism for applying ink to the printing plate and a dampening mechanism for supplying dampening fluid to an ink coated elastomeric form roll running in engagement with the printing plate, said dampening mechanism comprising an elastomeric transfer roll running in engagement with said ink coated form roll, said transfer roll having an ink accepting surface thereon whereby a coating of ink is formed on said transfer roll during operation of said press, means for supplying dampening fluid to said transfer roll to apply a film of dampening fluid to said transfer roll, and means for driving said transfer roll at a surface speed different from the surface speed of said form roll to create slippage between the elastomeric form roll and the elastomeric transfer roll to control the amount of dampening fluid applied to said plate, including means for varying the speed of said transfer roll.

2. In a lithographic printing press as defined in claim 1 wherein said means for driving said transfer roll comprises an unidirectional torque transmitting connection and means responsive to an overdriving of said connection by said trasfer roll for braking said transfer roll.

3. In a lithographic printing press as defined in claim 1 wherein said means for supplying dampening fluid to said transfer roll comprises a hydrophilic metering roll running in engagement with said elastomeric transfer roll and a pan for holding dampening fluid, said metering roll iprojecting into said pan to pick up a film of dampening uid.

4. In a lithographic printing press as defined in claim 1 further comprising means for supporting and moving said form roll to and from engagement with said plate and said transfer roll to and from engagement with said form roll when the latter is in a position clear of said plate comprising means to limit movement of said form roll toward said plate to determine the operating position thereof and means to adjust the distance between the axes of said form and transfer rolls to adjust the operating relationship therebetween.

5. A lithographic printing press as defined in claim 4 wherein said drive means comprises means enabling said form roll to drive said transfer roll at a speed greater than that of said drive means and means for braking the rotation of said transfer roll to the speed of said drive means in response to the roll being driven at a speed greater than the speed of said drive means.

6. A mechanism for applying a coating of a given material to a moving surface comprising a first roll having a surface formed of elastomeric material and rotating at a given surface speed, and means for applying said material to said first roll comprising a second roll having a surface running in engagement with said first roll, said surface of said second roll being formed of elastomeric material, and drive means operating at a predetermined speed for driving said second roll at a surface speed different from said first roll to control the amount of material being transferred to said first roll from said second roll including means enabling said first roll to drive said second roll at a higher speed than said drive means and means responsive to an overdriving of said second roll and said drive means by said first roll to brake said second roll to the speed of said drive means.

7. In a lithographic printing press having a printing plate mounted on a rotatable plate cylinder, inking mechanism for applying ink to the printing plate and a dampening mechanism for supplying dampening fluid to an ink coated form roll running in egagemet with the printing plate, said dampening mechanism comprising a transfer roll running in engagement with said ink coated roll, said transfer roll having an ink accepting surface thereon whereby a coating of ink is formed on said transfer roll during operation of said press, means for supplying dampening fluid to said transfer roll to apply a film of dampening fluod to said transfer roll, and means for driving said transfer roll at a surface speed different from said form roll to control the amount of dampening fluid applied to said plate, said means for driving said transfer roll comprising an unidirectional torque transmitting connection and means responsive to an overdriving of said connection by said transfer roll for braking said transfer roll including means responsive to a predetermined overrunning torque for performing a control function in addition to the braking of said transfer roll.

References Cited UNITED STATES PATENTS 2,260,040 10/ 1941 Levenhagen et a1.

10 Her. Landahl. Roberts. Tonkin et a1. Dahlgren. Burnett. Dahlgren.

U.S. Cl. X.R. 

